WO2009132643A2 - Roulement à rouleaux coniques et palier d'arbre pour au moins un roulement à rouleaux coniques - Google Patents

Roulement à rouleaux coniques et palier d'arbre pour au moins un roulement à rouleaux coniques Download PDF

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Publication number
WO2009132643A2
WO2009132643A2 PCT/DE2009/000634 DE2009000634W WO2009132643A2 WO 2009132643 A2 WO2009132643 A2 WO 2009132643A2 DE 2009000634 W DE2009000634 W DE 2009000634W WO 2009132643 A2 WO2009132643 A2 WO 2009132643A2
Authority
WO
WIPO (PCT)
Prior art keywords
bearing
shaft
tapered roller
shim
roller bearing
Prior art date
Application number
PCT/DE2009/000634
Other languages
German (de)
English (en)
Other versions
WO2009132643A3 (fr
Inventor
Jan Georgi
Martin STÜRZENBERGER
Original Assignee
Schaeffler Kg
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Schaeffler Kg filed Critical Schaeffler Kg
Publication of WO2009132643A2 publication Critical patent/WO2009132643A2/fr
Publication of WO2009132643A3 publication Critical patent/WO2009132643A3/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/60—Raceways; Race rings divided or split, e.g. comprising two juxtaposed rings
    • F16C33/605—Raceways; Race rings divided or split, e.g. comprising two juxtaposed rings with a separate retaining member, e.g. flange, shoulder, guide ring, secured to a race ring, adjacent to the race surface, so as to abut the end of the rolling elements, e.g. rollers, or the cage
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
    • F16C19/36—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers
    • F16C19/364—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/54—Systems consisting of a plurality of bearings with rolling friction
    • F16C19/546—Systems with spaced apart rolling bearings including at least one angular contact bearing
    • F16C19/547—Systems with spaced apart rolling bearings including at least one angular contact bearing with two angular contact rolling bearings
    • F16C19/548—Systems with spaced apart rolling bearings including at least one angular contact bearing with two angular contact rolling bearings in O-arrangement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C25/00—Bearings for exclusively rotary movement adjustable for wear or play
    • F16C25/06—Ball or roller bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2361/00—Apparatus or articles in engineering in general
    • F16C2361/61—Toothed gear systems, e.g. support of pinion shafts

Definitions

  • the invention relates to a tapered roller bearing and to a shaft bearing for at least one tapered roller bearing.
  • Such a tapered roller bearing is known for example from US 4,065,191 A. It has a bearing inner ring with a conical inner raceway and a bearing outer ring with a conical outer raceway.
  • the bearing inner ring and the bearing outer ring are rotatably supported about a common axis by means of rolling bearings designed as tapered rollers.
  • the rolling elements in turn are axially supported by means of a separate board body.
  • tapered roller bearings are used in pairs in the so-called X-arrangement or in the O-arrangement for shaft bearings.
  • X-arrangement or in the O-arrangement for shaft bearings.
  • O-arrangement is an O-arrangement of the two tapered roller bearings usual.
  • the two tapered roller bearings should be adjusted to each other to an optimized bearing preload or to an optimized bearing clearance.
  • an acceptable bearing preload or an acceptable bearing clearance can be achieved by a very precise production of all the bearing play influencing components (shaft, bearings, housing) and taking into account the probability in the combination of these components.
  • an optimized bearing preload or an optimized bearing play is desired, this must be adjusted by measuring the components and a number of shims, which are pushed onto the shaft between the two tapered roller bearings.
  • the known procedure for adjusting the bearing clearance or the bearing preload is associated with a great deal of work and binds the press required for this purpose by a possible repeated assembly or disassembly.
  • the invention is therefore based on the object, a Wälz- To make camp so that the setting of the bearing clearance or the bearing preload a shaft bearing with little effort and even with a tight fit of the bearing rings on the shaft without a press as a mounting device is possible.
  • a shim is arranged in a tapered roller bearing of the type mentioned between the board body and one of the two bearing rings.
  • Such shims are used in mechanical engineering to set the distance between individual components of a shaft bearing, in particular of rolling bearings to each other. In Germany, standard dimensions for shims are specified in DIN 988.
  • the bearing play or the bearing preload of the shaft bearing is remeasured. If necessary, the axial distance between the flange body and the bearing ring and thus the position of the rolling elements by inserting a number of shims of different thickness is changed.
  • the height of the tapered roller bearing is smaller by moving the other bearing ring along the tapered rollers.
  • the shims are only loosely fitted on the shaft. Furthermore, the board body is advantageously designed with an excess of the shaft. Thus, the shims and the body can be removed without effort by the use of a mechanical press manually or with a handling device and the total thickness of the shims correspondingly easy to adjust.
  • the board body is formed in cross-section L-shaped.
  • the transverse leg of the L is effective with its front side as a board to which the rolling elements create.
  • the vertical L-leg accommodates the number of shims between itself and the associated bearing ring.
  • the transverse leg is in the axial direction over the vertical leg of the L and engages in the space between the bearing inner ring and the bearing outer ring to specify the axial position of the rolling elements. How far the transverse limb projects beyond the vertical L-limb in the axial direction is predetermined by the thickness of the shim.
  • the raceway of the bearing ring can be performed to the end of the tapered rollers.
  • the entire roller width of the tapered rollers is utilized as a load-bearing surface.
  • the shim lies flat on the vertical L-leg and on the bearing ring. Due to the flat concerns of the shim also ensures that in the mounted state of the bearing the set axial play is maintained.
  • the rim ring can have any geometry and can also be formed on a more complex component.
  • the board body is preferably designed as a flange, which can be produced in a simple manner in a forming process.
  • the separate board body can be suitably adjusted with respect to material and surface texture regardless of the functional surfaces of the rolling bearing on its function as GleitVFjackungsbauteil for the rolling elements.
  • the board body for example, a coating.
  • friction-enhancing and / or positive-locking devices are provided which can be arranged on the side of the flange body facing the shim, on the side of the bearing ring facing the shim, or on at least one side of the shim.
  • the device is designed, for example, as a profiling, as a toothing, in particular as a Hirth toothing, as a coating or as an adhesive film. It is applied, introduced or molded on the board body, on the bearing ring or on the shim.
  • the shims and / or the board body expediently by form elements, in particular by grooves, by teeth or by Grooves or elastically formed by their material, so that for an adjustment of the bearing preload or the bearing clearance no replacement of the at least one shim must be made.
  • the bearing clearance / preload can then be adjusted by tightening the shaft fitting more or less strongly.
  • a change in distance between the board body and the bearing ring is possible in the context of their elasticity.
  • the object is further achieved by a shaft bearing with a housing, with a shaft and with at least one tapered roller bearing according to one of claims 1 to 7.
  • the shaft is mounted on the tapered roller bearing in the housing.
  • the bearing inner ring is expediently pressed onto the shaft in order to ensure a tight fit of the bearing inner ring on the shaft.
  • the bearing outer ring is expedient pressed in the housing and thus arranged in the housing against rotation. The pressing of the bearing inner ring on the shaft or the compression of the bearing outer ring in the housing are common practice when mounting a roller bearing.
  • the board body is provided with a transition fit with respect to the shaft, which allows easy assembly and disassembly.
  • the number of shims and the flange body can be postponed on the shaft and reassembled in retrospect with the pressed-in roller bearing already mounted.
  • the distance between the body and firmly pressed bearing ring can be changed at any time in retrospect by replacing the shims to adjust the optimal bearing clearance and the optimal bearing preload.
  • the rolling bearing is clamped in the axial direction by means of a shaft nut by means of a bracing device.
  • the board body with the shim is fixed against the corresponding bearing pressed ring, so that the set axial play is maintained even in the final assembly.
  • a receptacle for bracing the flange body against one of the two bearing rings is provided on the side of the flange body facing away from the washer.
  • pins or the like may be provided which produce a positive connection between the flange body and the shaft and thus prevent rotation of the rim body relative to the shaft. In this way, a positive and non-positive fixing of the board body is achieved in its position.
  • FIG. 2 shows a detail of one of the two roller bearings from FIG. 1
  • FIG. 3 shows a shim in a plan view
  • FIG. 4 shows the shim of FIG. 2 in a sectioned side view
  • FIG. 5 shows a pinion shaft bearing with two roller bearings.
  • FIG. 1 shows schematically in a sectional side view a detail of a shaft bearing 1, in which a shaft 2 is rotatably mounted in a housing 5 by means of a first rolling bearing 3 and a second rolling bearing 4.
  • the two designed as tapered roller bearings rolling bearings 3, 4 are mounted in the so-called O-arrangement.
  • the first designed as a tapered roller bearing bearings 3 has a bearing inner ring 6 with a conical inner race 6 'and a bearing outer ring 7 with a conical outer race 7' on.
  • the bearing inner ring 6 and the Bearing outer ring 7 are mounted by means of a plurality of rolling elements arranged between them 8 about a common axis which coincides in the assembled state with the central longitudinal axis 9 of the shaft 2.
  • the second rolling bearing 4 is in turn designed as a tapered roller bearing with a conical inner race 11 'having bearing inner ring 11 and a conical outer race 12' having bearing outer ring 12.
  • the bearing inner ring 11 and the bearing outer ring 12 of the second rolling bearing 4 are also mounted by means of rolling elements 13 designed as tapered rollers about a common axis, which coincides in the final assembled state with the central longitudinal axis 9 of the shaft 2.
  • the leadership of the rolling elements 8,13 takes place in each case by means of a bearing cage 10.
  • the axial position of the bearing rings 6.7 is fixed by appropriate abutment shoulders in the housing and on the shaft
  • the second rolling bearing 4 is a tapered roller bearing of conventional design.
  • the first rolling bearing 3 has a board body designed as a rim 15 with an L-shaped cross-section.
  • This board body 15 is shown in Fig. 2 in an enlarged detail.
  • the pointing in the axial direction 14 transverse leg 16 of the L is effective as with its front side to the rolling elements 8 abutting edge and specifies the axial clearance of the rolling bearing 8.
  • the vertical L-leg 17 receives one or more shims 18 between itself and the bearing inner ring 6. In the figures, for the sake of simplicity, only a single shim is shown.
  • the bearing inner ring 6, the board body 15 and the shim 18 support and thus lead together the rolling elements 8 and thus jointly perform the same function as the one-piece bearing inner ring 11 of the second rolling bearing 4th
  • Fig. 3 shows the shim 18 in a plan view.
  • the fitting disc of Fig. 3 is shown in a sectional side view.
  • the shim 18 is uniquely characterized by its outer diameter 19, by its inner diameter 20 and by its thickness 21.
  • the board body 15 and the shim 18 allow adjustment of the position of the rolling elements 8 within the rolling bearing 3 in the axial direction 14.
  • the board body 15 is equipped with a transition fit. In other words, it can be postponed without significant resistance to the shaft 2.
  • the pushed onto the shaft 2 shims 18 are provided opposite the shaft 2 with an oversize.
  • the rolling elements 8 are moved with mounted roller bearing 3 within the camp.
  • the shim 18 is pushed from the direction shown by arrow 22 in Fig. 1 on the shaft 2 until it rests flat against the bearing inner ring 6.
  • the board body 15 is pushed onto the shaft 2, until it also lies with its the shim 18 side facing flat against this.
  • the board body 15 is braced against the bearing inner ring 6 a in Figs. 1 and 2, not shown bracing device.
  • the transverse leg 16 of the flange 15 engages in the inner race 6 'of the rolling bearing 3 and thus provides the position of the rolling elements 8 in the axial direction 14.
  • Fig. 5 shows the detail of Fig. 2 without shims between the board body 15 and the bearing inner ring 6.
  • the trained as a tapered rollers 8 move in the direction of arrow 22.
  • the bearing clearance compared to FIG. 2 is reduced.
  • the overall height 23 'of the rolling bearing 3 increases.
  • Fig. 6 shows a formed as a pinion shaft bearing shaft bearing 1 in a sectional side view.
  • two tapered roller bearings 3, 4 are provided, which are arranged in an O-arrangement.
  • the conditions correspond to those of the schematic view in Fig. 1.
  • the first rolling bearing 3 is provided with an additional board body 15 and a held between the board body 15 and its bearing inner ring 6 shim 18.
  • the second rolling bearing 4 is formed as a conventional tapered roller bearing.
  • a bracing device 24 is provided, which engages with a plurality of arms 25 in the receptacles 26 on the side facing away from the shim of the rim body 15.
  • the position of the bracing device 24 in the axial direction 14 is secured by means of a shaft nut 27.
  • the predetermined by the shim 18 and the rim 15 axial clearance of the rolling elements 8 is also given in final assembled state.
  • the shim 18 facing side of the flange body 15, the shim 18 facing side of the bearing inner ring 6 and the two sides of the shim 18 are provided with a profiling to increase the friction between the individual bearing components 6, 15, 18. In this way, the board body 15 is held against rotation on the bearing inner ring 6.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)
  • Support Of The Bearing (AREA)

Abstract

Le roulement à rouleaux coniques (3) selon la présente invention présente une bague de roulement intérieure (6) comprenant un chemin de roulement intérieur conique (6') et une bague de roulement extérieure (7) comprenant un chemin de roulement extérieur conique (7'). Une pluralité de corps roulants (8) sous forme de rouleaux coniques sont prévus pour le montage à rotation de la bague de roulement intérieure (6) et de la bague de roulement extérieure (7) autour d'un axe commun (9). Les corps roulants (8) sont maintenus axialement par un corps d'épaulement (15). Une rondelle d'ajustage (18) est placée entre le corps d'épaulement (15) et l'une des bagues de roulement (6) pour le réglage du jeu axial des corps roulants (8) dans la direction axiale (14).
PCT/DE2009/000634 2008-05-02 2009-05-02 Roulement à rouleaux coniques et palier d'arbre pour au moins un roulement à rouleaux coniques WO2009132643A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102008021884.7 2008-05-02
DE102008021884A DE102008021884A1 (de) 2008-05-02 2008-05-02 Kegelrollenlager und Wellenlagerung für zumindest ein Kegelrollenlager

Publications (2)

Publication Number Publication Date
WO2009132643A2 true WO2009132643A2 (fr) 2009-11-05
WO2009132643A3 WO2009132643A3 (fr) 2010-01-28

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PCT/DE2009/000634 WO2009132643A2 (fr) 2008-05-02 2009-05-02 Roulement à rouleaux coniques et palier d'arbre pour au moins un roulement à rouleaux coniques

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Country Link
DE (1) DE102008021884A1 (fr)
WO (1) WO2009132643A2 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111853054A (zh) * 2019-04-30 2020-10-30 斯凯孚公司 包括三个同心圈的滚动轴承

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008039477A1 (de) 2008-08-23 2010-02-25 Schaeffler Kg Ritzelwellenanordnung und Fahrzeuggetriebe mit der Ritzelwellenanordnung
DE102010011282A1 (de) 2010-03-13 2011-09-15 Schaeffler Technologies Gmbh & Co. Kg Wälzlageranordnung mit einem Kegelrollenlager
DE102010054903A1 (de) * 2010-12-17 2012-06-21 Schaeffler Technologies Gmbh & Co. Kg Kegelrollenlager mit mehrteiligem Innenring
DE102012217506B4 (de) * 2012-09-27 2014-07-10 Schaeffler Technologies Gmbh & Co. Kg Lageranordnung für ein Getriebe
DE102015201506B4 (de) * 2015-01-29 2023-02-09 Aktiebolaget Skf Lageranordnung
DE102015220013A1 (de) * 2015-10-15 2017-04-20 Aktiebolaget Skf Lageranordnung

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR583067A (fr) * 1923-07-02 1925-01-06 Support ou palier réglable pour pression et poussée
FR1355878A (fr) * 1963-03-18 1964-03-20 Skf Svenska Kullagerfab Ab Perfectionnements aux roulements à rouleaux
GB1187769A (en) * 1966-06-02 1970-04-15 Skf Kugellagerfabriken Gmbh Improvements in or relating to Rolling Bearings and to Race Rings Therefor
JPS53125542A (en) * 1977-04-08 1978-11-01 Ntn Toyo Bearing Co Ltd Single row type roller bearing with buckling ring

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4065191A (en) 1976-05-13 1977-12-27 Skf Industries, Inc. Roller skew control for tapered roller bearings

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR583067A (fr) * 1923-07-02 1925-01-06 Support ou palier réglable pour pression et poussée
FR1355878A (fr) * 1963-03-18 1964-03-20 Skf Svenska Kullagerfab Ab Perfectionnements aux roulements à rouleaux
GB1187769A (en) * 1966-06-02 1970-04-15 Skf Kugellagerfabriken Gmbh Improvements in or relating to Rolling Bearings and to Race Rings Therefor
JPS53125542A (en) * 1977-04-08 1978-11-01 Ntn Toyo Bearing Co Ltd Single row type roller bearing with buckling ring

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111853054A (zh) * 2019-04-30 2020-10-30 斯凯孚公司 包括三个同心圈的滚动轴承

Also Published As

Publication number Publication date
WO2009132643A3 (fr) 2010-01-28
DE102008021884A1 (de) 2009-11-05

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